Variable speed transmission



Jan. 3, 1939.

P. SIMONDS VARIABLE SPEED TRANSMISSION Filed Jan. 12, 1937 l6 Sheets-Sheet l Fig. 1-.

22 I as 23 4 2 .J 34 r I i J 3/ I l z I V M I av l l I 40 1 i I I If i r j 37 i l l i I INVENTOR PAUL SJMDNDS MORNEY Jan. 3, 1939. P4 SIMONDS VARIABLE SPEED TRANSMIS SION Filed Jan. 12, 1937 16 Sheets-Sheet 3 Q 2 97 W w 7. m @4 /////////-////X/ M kW/fl lfd/Iffl/J m w 7 4 7 ..\\\\\\\\M .W u I O 5 9 7 5 WM @J/ INVENTOR PAUL SIMEINDS ATTORNEY.

Jan. 3, 1939.

P. SIMONDS VARIABLE SPEED TRANSMISSION Filed Jan. 12, 1957 16 Sheets-5heet 5 INVENTOR PAL- SIMUNBS BY ATTORNEY- Jan.3,19f39 P MONDS I 2,142,700

I VARIABLE SPEED TRANSMISSION Filed Jan. 12, 1937 16 Sheets-Sheet 6 INVENTOR PAUL SIMEINDS ATTORNEY.

P. SIMONDS Jan. 3, 1939.

VARIABLE SPEED TRANSMISS ION l6 Sheets-Sheet 7 Filed Jan. 12, 1937 u lull/1% S m W TM N m m V m T L/ vU Y PB Jan. 3, 1939. F. SIMONDS VARIABLE SPEED TRANSMISSION Filed Jan. 12, 1937 16 Sheets-Sheet 8 INVENTOR F ALI SI MENUS Jan. 3, 193 9. I P. SIMONDS 2,142,700

VARIABLE SPEED TRANSMISSION I Filed Jan. 12, 1957 16 Sheets-Sheet 9 lyv w qw Jan. 3, 1939. R SMONDS 2,142,700

VARIABLE SPEED TRANSMISSION Filed Jan. 12, 1937 16 Sheets-Sheet l0 ID- V 'INVENTOR P XUL SIMEINDS ATTO-RNEY- P. SIMONDS VARIABLE SPEED TRANSMISSION Jan. 3, 1939.

16 Sheets-Sheet ll Filed Jan. 12, 1957 INVENTOR P'ALIL SIMBNDS BY I Jan. 3, 1939.

P. SIMONDS VARIABLE SPEED TRANSMISSION Filed Jan. 12, 1937 16 Sheets-Sheet 12 lNVENT OR PAUL Smumos BY ATTORNEY.

Jan. .3, 1939.

P. SIMONYDS 2,142,700

VARIABLE SPEED TRANSMI S S ION Filed Jan. 12, 1937 16 Sheets-Shet 13 v INVENTOR PBAUL. SIMEINDS 4. Y I I 1 ATTORNEY.

7 Jan. 3, 1939. P SIMONDS VARIABLE SPEED TRANSMISSION- l6 Sheets-Sheet 14 Filed Jan. 12, 1937 INVENTOR P AU Jan. 3, 1939. P; SIMONDS VARIABLE SPEED TRANSMISSION 16 Sheets-Sheet 15 Filed Jan. 12, 1937 mvENTOR PAUL Smnwns TTORNEY.

Jan. 3, 1939;

F" SIMONDS VARIABLE SPEED TRANSMISSION l6 Sheets-Sheet 16 Filed Jan. 12, 1937 INVENTOR PAUL SIMEINDS Patented Jan. 3, 1939 UNITED STATES PATENT OFFICE 18 Claims.

This invention relates to variable speed transmissions of the type which will transmit motion from a driving element to a driven element and permit the speed of the driven element to be a varied steplessly between a minimum and a maximum speed.

A hydraulic transmission, consisting primarily of a pump and a hydraulic motor, is capable of varying the speed of a driven element steplessly from zero to maximum in either direction of rotation but the mechanical transmissions now in use either employ friction drives, so that the driven element is not positively driven, or they are incapable of varying the speed of the driven element steplessly from zero to maximum.

The present invention has as an object to provide a mechanical transmission which will positively drive a driven element and vary the speed thereof steplessly from zero to maximum.

Another object is to provide a positive drive, stepless, mechanical transmission which is reversible.

Other objects and advantages will appear from the description hereinafter given of a transmission in which the invention is embodied.

The invention is exemplified by the transmission shown somewhat schematically in the accompanying drawings in which the views are as follows:

Fig. l is a top plan view of the transmission.

Fig. 2 is a central vertical section taken on the line 22 of Fig. 1.

Fig. 3 is a vertical section taken on the line 33 of Fig. 1.

Fig. 4 is a vertical section taken on the line 4-4 of Fig. 1.

Fig. 5 is a vertical section taken on the line 55 of Fig. 2.

Fig. 6 is a vertical section taken on the line 66 of Fig. 2.

Fig. 7 is a vertical section taken on the line of Fig. 2.

Fig. 8 is a vertical section taken on the line 8--8 of Fig. 2. I

Fig. 9 is a vertical section taken on the line 89 of Fig. 2..

Fig. 10 is a vertical section taken on the line lfi-Jll of Fig. 2.

Fig. 11 is a vertical section taken on the line l!|l of Fig. 2.

Fig. 12 is a vertical section taken on the line 12-42 of Fig. 2.

Fig. 13 is a vertical section taken on the line l3l3 of Fig. 2. 7

Fig. 14 is a vertical section taken on the line 14-44 of Fig. 2.

Fig. 15 is a vertical section taken on the line |5l5 of Fig. 2.

Fig. 16 is a vertical section taken on the line 5 |6-l6 of Fig. 2.

Fig. 1'? is a diagram of the pitch lines of a pair of intermeshing irregular shaped gears one of which will rotate at a speed which will vary uniformly relative to the speed of the other gear when one of the gears is driven.

In order to simplify the views and in order that the operation of the transmission may be more readily understood, only the parts lying substantially upon or immediately behind the section 16 lines have been shown in Figs. 2 to 16 inclusive.

The transmission has its mechanism carried by a frame composed of suitable members, such as four vertical frame members 2 I, 22, 23 and 24 and six spacers 25, 26, 21, 28, 29 and 30 which retain the frame members in fixed positions relative to each other.

Motion is transmitted to the transmission from an external source of power (not shown) through an input shaft 3| which is journaled in frame members 2|, 22, 23 and 24 as shown in Fig. 4. For the purpose of explanation, let it be assumed that shaft 3| is being driven at a constant speed of 900 R. P. M. in a counterclockwise direction as viewed in Figs. 5 to 16 inclusive. 30

Motion is transmitted from the transmission to the machine to be driven through an output shaft 32 which is journaled in frame member 2| and has its inner end reduced in diameter and journaled in the end of a shaft 33 which is journaled in frame members 22 and 24 as shown in Fig. 2.

Motion is transmitted to output shaft 32 from input shaft 3| through mechanism to be presently described. This mechanism enables output shaft 32 to be driven in either direction at a speed which may be varied steplessly from zero to maximum. With the arrangement shown, the maximum speed of output shaft 32 is A of the speed of input shaft 31, or 50 R. P. M., so that shaft 32 45 may be rotated in either direction at any speed from zero to 50 R. P. M.

Input shaft 3| (Fig. 4) has three gears 34, 35 and 36 fixed thereon to rotate therewith. Gear 34 meshes with a gear 31 (Figs; 1, 2 and 5) which is journaled upon shaft 32 and has a bevel gear 32 fixed thereto to rotate therewith. The ratio of gear 34 to gear 31 is 1:3 so that gears 31 and 38 will be driven at a constant speed of 300 R. P. M. in a clockwise direction when input shaft 3| is being driven at 900 R. P. M. in a counterclockwise direction.

Bevel gear 38 forms one input leg of a reversing differential which is shown as consisting primarily of gear 38, a similar bevel gear 39 which forms the other input leg of the differential and is fixed'upon shaft 33 at the end thereof, a spider 48 which is arranged between gears 38 and 39 and fixed upon shaft 32, and two spider pinions 4| and 42 which are suitably journaled upon spider 4D and mesh with both of gears 38 and 39.

It is obvious that, if gears 38 and 39 are driven in opposite directions, spider 40 and output shaft 32 will be driven at a speed equal to one-half the difference between the speeds of gears 38 and 39 and in a direction dependent upon which of gears 38 and 39 is rotating the faster.

In the arrangement shown and with input shaft 3| being driven at a constant speed of 900 R. P. M. in a counterclockwise direction, shaft 33 is adapted to be driven in a counterclockwise direction at any speed between 200 R. P. M.-and 400 R. P. M. as will presently be explained. With the transmission adjusted as shown, shaft 33 and the gear 39 fixed thereto-will be rotated at a constant speed of 400 R. P. M. in a counterclockwise direction.

With gear 38 rotating in a clockwise direction at 300 R. P. M. and gear 39 rotating in a counterclockwise direction at 400 R. P. M., output shaft 32 will be rotated in a counterclockwise direction at R. P. M. If the transmission is adjusted until gear 39 is rotating at 300 R. P. M., output shaft '32 will remain stationary for the reason that gear 38 will be rotating at the same speed but in the opposite direction.

If the transmission is further adjusted until gear 38 is rotating at 200 R. P. M., output shaft 32 will be rotated at 50 R. P. M. in a clockwise direction for the reason that gear 38 is rotating 100 R. P. M. faster in a clockwise direction than gear 39 is rotating in a counterclockwise direction.

Gear 35 on input shaft 3| (Figs. 4 and 6) meshes with and drives a gear 46 (Figs. 2 and 6) which is journaled upon shaft 33 and has a bevel gear 41 fixed thereto. Gears 35 and 46 have the same pitch diameter so that gears 56 and 41 are driven from shaft 3| in a clockwise direction at 900 R. P. M.

Gear 4? forms one leg of a speed adjusting differential which is shown as consisting primarily of gear 41', a similar bevel gear 48 which is journaled upon shaft 33, a differential gear 58 which is journaled upon shaft 33 between gears 81 and 48, and two spider pinions 5| and which are suitably journaled within openings 52 formed diametrically opposite each other in gear 59. Each pinion 5| extends through an opening 52 and meshes with both of gears 41 and 48.

Gear 58 meshes with a gear 53 and is held thereby in the position shown which is the correct position to cause output shaft 32 to be driven at 50 R. P. M. in a counterclockwise direction when input shaft 3| is driven at 900 R. P. M. in a counterclockwise direction. When gear 56 is held stationary, the transmission is adjusted as shown and input shaft 3| is rotating at 900 R. P. M. in a counterclockwise direction, bevel gear 48 will be rotated at 900 R. P. M. in a counterclockwise direction.

Before continuing the description of the driving mechanism, it will be necessary to describe the mechanism for adjusting the transmission vary the speed of output shaft 32 relative to rotate therewith, and both of these gears are journaled upon a stub shaft 58 fixed in frame member 22.

Worm gear 51 meshes with a worm 6| which is fixed upon a shaft 52 having one end thereof journaled in frame spacer 26 and the other end thereof journaled in a bracket 53 carried by and depending from frame spacer 25.

Shaft 62 has a helical gear 64 fixed thereon and in mesh with a helical gear 65 fixed upon an adjusting shaft 66 (Fig. 1) which is journaled in suitable bearings carried by frame members 22, 23 and 24. Shaft 66 is provided at one of its ends with a hand wheel 6'! by means of which it may be rotated to vary the speed and/or the direction of rotation of output shaft 32 as will be presently explained.

Shaft 66 has also fixed thereon four helical gears '58, 1|, (2 and 73. Gear 70 meshes with a helical gear I4 (Fig. 9) fixed upon an adjusting shaft 15 which is journaled in suitable bea ings arranged in frame spacers 25 and 26. Gear ll meshes with a helical gear 16 (Fig. 11) fixed upon an adjusting shaft 11 which is journaled in suitable bearings arranged in frame spacers 25 and 26.

Gear 12 meshes with a helical gear 18 (Fig. 13) fixed upon an adjusting shaft 19 which is journaled in suitable bearings arranged in frame spacers 25 and 26. Gear 73 meshes with a helical gear 88 (Fig. 15) fixed upon an adjusting shaft 8| which is journaled in' suitable bearings arranged in frame spacers 25 and 26. Rotation of hand wheel 6! will thus cause adjusting shafts 62, 15, 11, 18 and 8| to rotate simultaneously.

Adjusting shaft 15 (Fig. 9) has a worm fixed thereon and in mesh with a ring gear 86 which is supported by and rotatable in suitable guide bearings carried by frame spacers 21, 23 and 30. Worm 85 normally holds ring gear 85 stationary but will rotate it when hand wheel 5"! is rotated.

The internal teeth of ring gear 86 mesh with four gear segments 81, 88, 89 and 99 which are arranged 90 apart and normally held by ring gear 86 in stationary positions but will be swung by ring gear 86 to new positions when hand wheel 67 is rotated. Gear segment 81 is journaled upon shaft 55 and gear segments 88, 85 and 98 are journaled, respectively, upon three shafts (Fig. 2), 92 (Fig. 4) and 93 (Fig. 3) which are journaled in frame members 22 and 23.

Adjusting shaft 1'! (Fig. 11) has a worm 95 fixed thereon and in mesh with a ring gear 93 which is supported by and rotatable in suitable guide bearings carried by frame spacers 21, 28 and 30. Worm 95 normally holds ring gear 96 stationary but will rotate it when hand wheel 61 is rotated.

The internal teeth of ring gear 86 mesh with four gear segments 91, 98, 99 and I00 which are normally held by ring gear 96 in stationary positions but will be swung by it into new positions when hand wheel 61 is rotated. Gear segments I .-2,142,7oo

-91, 98, "99 and 1:00 am vjournaled, respectively,

upon shafts 255,?9I, 92 .and 93.

Adjusting shaft '19 (Fig. 13) has a worm 405 fixed thereon and in mesh with a ring gear 406 which is supported byandrotatablein suitable guide bearings carried by frame spacers '24, 28 and .30. Worm I65 normally 'tholds 'ring gear I06 stationary but willrotate it when'hand wheel 3! is rotated.

The internal teeth of ring-gear 4.06 mesh with four gear segments :IIl I, 108, H19 .and .I II) which are arranged 90 apart and normally held by ring gear I06 in stationary positions but will be swung by it into new positions when hand wheel 61 is rotated. Gear segments I01, I98, H19 and III? are journaled, respectively, uponifour shafts III, H2 (Fig.2), IJI3 (Fig. 4) and H4 (Fig. 3) which are journaled in frame members 23 and 24 in axial a'linement, respectively, with shafts 55, 9!,92 and93.

Adjustingsshaft 8| (Fig.15) has aworm I20 fixed thereon andinmesh with aring gear -]2I which is supported by and rotatable in suitable guide bearings carried by frame spacers 121, .28 and .39. Worm Itzflnormally holds ring gear I.2I stationary but will rotateit when hand wheel 61 is rotated.

Theinternal teeth of ring gear I2I mesh with four gear segments I22, I23, I24 and I25 which are normally held in stationary positions by'ring gear 1'2! but will be swung by it into new pcvsitions when hand wheel 61 is rotated. Gear segments I22, I23, I24 and I25 are .journaled, respectively, upon shafts III, H2, H3 and H4.

The functions of the above described parts of the adjusting mechanism will be explained after the remainder of the driving mechanism has been described and the operation of the transmission explained.

Referring first to Figs. 4and 16,,gear 36 on input shaft 3I meshes with an idler gear I39 which is journaled upon shaft III (Fig. 2). Gear I39 meshes with and drives a gear I3l which is journaled upon shaft 33 and has an irregular shaped gear I32 fixed thereto to rotate therewith.

Gear I3! has the'same pitch diameter as gear- 36 so that it and gear I32 are rotated upon shaft 33 at 900 R. P. M. in a counterclockwise direction in unison with shaft 31.

Irregular shaped gear I32 meshes with and drives four complementary irregular shaped gears I33, I34, I35 and I36 which are identical to each other and fixed,respectively, upon shafts III, H2, H3 and -I I4 todrive the-same.

Irregular shaped gear I32 is exactly the same as an irregular shaped gear I42 (Figs. 2 and '7) which is journaled upon shaft 33 and fixed to bevel gear 48 so that it is rotated therewith at 900 R. P. M. in a counterclockwise direction when the transmission is adjusted as shown and input shaft 3I is rotating at the same speed in a counterclockwise direction as previously explained.

Irregular shaped gear I42 meshes with and drives four complementary irregular shaped gears I43, I44, I45 and I46 which are fixed, respectively, upon shafts 55 and 9| (Fig. 2), shaft 92 (Fig. 4) and shaft 93 (Fig. 3) to drive the same. Irregular shaped gears I43, I44, I45 and I46 are identical to each other and to irregular shaped gears I33, I34, I35 and I36.

The above mentioned irregular shaped gears are so designed that, when a driving gear I 32 or I42 is rotating in one direction at a constant speed, the driven gears meshing therewith will be rotated in the opposite direction at speeds :which vary uniformly from one-third to one and two-thirds times the speed of the driving gear.

Consequently, when gear I32 is rotated at 900 R. P. M. in a counterclockwise direction, gears I33, I34, I35 and I36 and shafts III, H2, H3

and H4 will be rotated in a clockwise direction at speeds which vary uniformly from 300 R. P. M. to 150'0'R. P. Mpand, when gear I42 is rotating at 1900 R. P. M. in a counterclockwise direction, gears I43, I44, I45 and I46 and shafts 55, 9|, 9'2 and 93 willb'e rotated in a clockwise direction atspeeds which vary uniformly from 300 R. P. M.

to 1500 R. P. M.

In the transmission shown, the above de-:

scribed .irregular shaped gears have pitch lines :of the shapes shown in Fig. 17 and each gear is symmetrical about a line coinciding with its rnsx+ min max min 2 1nin+ 180 In the formulas:

Ris the pitch radius of gear DR at angle A.

R1 is the pitch radius of gear DN at angle A1.

.A isthe angle from the minimum radius of gear DR with a maximum of 180 (the gear being symmetrical) A1 is the angle from the maximum radius of gear DN with a maximum of 180 (the gear being symmetrical) 'C is the distancebetween gear centers in inches. 'Vmm is the minimum angular velocity of gear DN. For simplicity, let the value he 1. Vmsx is the maximum angular velocity of gear 'DN. The value may be the desired multiple of Vrnin.

in INE 2 will always be equal to the velocity of gear DR because the average speed-of gear DN is equal to the speed of gear DR.

With the irregular shaped gears designed .and driven as explained above, each driven gear will beaccelerated from 300 RP. M. to 1500 R. P. M. during one-half of each revolution and be decelerated from 1500 R. P- M. to 300 R. P. M. during the other half of each revolution. Before explaining how these varying speeds are utilized, the mechanisms driven by the irregular shaped gears will be described.

As previousy explained, irregular shaped gears I93, 34, I35 and i% (Fig. 16) are fixed upon and drive shafts III, H2, H3 and H4 respectively, and irregular shaped gears I43, I44, I45 and I46 (Fig. 7') are fixed upon and drive shafts 55, 9|, "92 and 93 respectively. Each of these shafts Ehas two mutilated gears fixed thereon and adapted to intermittently mesh with two other gears.

Mutilated gears II, I52, I53 and I54 (Fig. 8) are fixed, respectively, upon shafts 55 and SI (Fig. 2), shaft 92 (Fig. 4) and shaft 93 (Fig. 3). Mutilated gears I55, I56, I51 and I58 (Fig. 11) are also fixed, respectively, upon shafts 55, 9I, 92 and 93.

Mutilated gears I6I, I62, I63 and I64- (Fig. 12) are fixed, respectively, upon shafts III and H2 (Fig. 2), shaft II3 (Fig. 4) and shaft II4 (Fig. 3). Mutilated gears I65, I66, I61 and I68 (Fig. 15) are also fixed upon shafts III, H2, H3 and H4 respectively.

Mutilated gears I51, I52, I53 and I54 (Fig. 8) are adapted to mesh, respectively, during a part of each revolution with gears I1I, I12, I13 and I14; gears I55, I56, I51 and I58 (Fig. 11) are adapted to mesh, respectively, during a part of each revolution with gears'I15, I16, I11 and I18; gears I6I, I62, I63 and I64 (Fig. 12) are adapted to mesh, respectively, during a part of each revolution with gears I8I, I82, I83 and I84; and gears I65, I66, I61 and I68 (Fig. 15) are adapted to mesh, respectively, during a part of each revolution with gears I85, I86, I81 and I88.

Gears I1I, I12, I13 and I14 (Fig. 8) are fixed, respectively, upon the left ends of shafts I 9|, I92, I93 and I94 which are journaled, respectively, in gear segments 81, 88, 89 and 90 (Fig. 9) and have gears I95, I96, I91 and I98 fixed, respectively, upon the right ends thereof.

Gears I15, I16, I11 and I18 (Fig. 11) are fixed, respectively, upon the right ends of shafts 20I, 202, 203 and 204 which are journaled, respectively, in gear segments 91, 98, 99 and I00 and have gears 205, 206, 201 and 208 (Fig. fixed, respectively, upon the left ends thereof.

Gears I8I, I82, I83 and I84 (Fig. 12) are fixed, respectively, upon the left-ends of shafts 2II, 2I2, 2I3 and 2I4 which are journaled, respectively, in gear segments I01, I08, I09 and H0 (Fig. 13) and have gears 2I5, 2I6, 2H and 2I8 fixed, respectively, upon the right ends thereof.

Gears I85, I86, I81 and I88 (Fig. are fixed, respectively, upon the right ends of shafts 22I, 222, 223 and 224 which are journaled, respectively, in gear segments I22, I23, I 24 and I25 and have gears 225, 226, 221 and 228 (Fig. 14) fixed, respectively, upon the left ends thereof.

Gears I95, I96, I91 and I98 (Fig. 9) mesh, respectively, with wide-faced gears 23I, 232, 233 and 234 which are journaled, respectively, upon shafts 55 and BI (Fig. 2), shaft 92 (Fig. 4) and shaft 93 (Fig. 3). Gears 205, 206, 201 and 208 (Fig. 10) also mesh, respectively, with wide-faced gears 23I, 232, 233 and 234.

Gears 2I5, 2I6, 2H and 2I8 (Fig. 13) mesh, respectively, with wide-faced gears 235, 236, 231 and 238 which are journaled, respectively, upon shafts III and H2 (Fig. 2), shaft II3 (Fig. 4) and shaft II4 (Fig. 3), Gears 225, 226, 221 and 228 (Fig. 14) also mesh, respectively, with widefaced gears 235, 236, 231 and 238.

Each of wide-faced gears 23I to 238 has a groove formed in its periphery to clear another gear to be presently described. The mutilated mating gear, the wide faced gear journaled upon the same shaft will be rotated at the same speed as the shaft and through an angular distance determined by the number of teeth on the mutilated gear, which, in the transmission as shown, is 60.

Wide-faced gears 23I and 232, (Figs. 2 and 10) also mesh with and drive a gear 24I journaled upon shaft 33 and meshing with a gear 242 which is fixed upon a shaft 243 (Fig. 4) journaled in frame members 22, 23 and. 24. The ratio of gears 23I and 232 to gears 241 and 242 is 1:3 so that gears 24I and 242 are driven at one-third the speeds of gears 23I and 232.

Gear 24I (Figs. 2 and 10) has a bevel gear 244 fixed thereto to rotate therewith. Bevel gear 244 meshes with two spider pinions 245 and 246 journaled upon suitable trunnions carried by a spider 241 which is fixed upon shaft 33 as shown in Fig. 2. Pinions 245 and 246 mesh with a bevel gear 248 (Figs. 2 and 12) which is identical to gear 244 and fixed for rotation with a spur gear 249 (Fig. 13) which is identical to gear 24I and journaled upon shaft 33. These bevel gears, pinions and spider form a speed leveling differential the function of which will be presently explained.

Gear 249 (Fig. 13) meshes with wide faced pinions 231 and 238 and with a gear 252 which is fixed upon a shaft 253 (Fig. 3) journaled in frame members 22, 23 and 24.

Shaft 253 also has a gear 254 (Fig. 9) fixed thereon and in mesh with a gear 255 which is journaled upon shaft 33 and meshes also with wide faced gears 233 and 234.

Wide faced pinions 235 and 236 (Figs. 2 and 14) also mesh with and drive a gear 26I which is journaled upon shaft 33 and meshes with a gear 262 fixed upon shaft 243 (Fig. 4).

From the foregoing, it' will be noted that each 'of shafts 55, 9|, 92, 93, Ill, H2, H3 and H4 has two mutilated gears fixed thereon and one wide faced gear journaled thereon, and that with the transmission adjusted as shown, each of the mutilated gears fixed on a shaft drives during one-sixth of each revolution the wide faced gear journaled upon the same shaft.

As previously explained, wide faced gears 23I and 232 (Fig. 10) mesh with gear 24I which is fixed to the bevel gear 244 of the speed leveling differential, wide faced gears 235 and 236 (Fig. 14) mesh with gear 264 which is journaled upon shaft 33, and gears 242 and 262 (Figs. 10 and 14) are both fixed upon shaft 243 and mesh, respectively, with gears 24I and 26I so that bevel gear 244 is rotated by motion transmitted thereto periodically from shafts 55, 9|, III and H2.

1 Also as previously explained, wide faced gears 231 and 238 (Fig. 13) mesh with gear 249 which is fixed to the bevel gear 248 of the speed leveling differential, wide faced gears 233 and 234 (Fig. 9) mesh with gear 255 which is journaled upon shaft 33, and gears 252 and 254 (Figs. 13 and 9) are both fixed upon shaft 253 and mesh, respectively, with gears 249 and 255 so that bevel gear 248 is rotated by motion transmitted thereto periodically from shafts 92, 93, H3 and H4.

As previously explained, irregular shaped gear I32 (Fig. 16) will be driven at 900 R. P. M. in a counterclockwise direction through gears 36, I30 and I3I so that the irregular shaped gears I33 to I36 meshing with gear I32 will rotate shafts HI to H4 in a clockwise direction at speeds which vary uniformly from 300 R. P. M. to 1500 R. P. M., and irregular shaped gear I42 (Fig. 7) will be driven at 900 R. P. M. in a coun- 

